JP2006300213A - Torque cam device and belt-type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a torque cam device and a belt type continuously variable transmission capable of inhibiting the generation of a time lag and a shock in transmitting torque when a driving state is changed. <P>SOLUTION: This torque cam device comprises a first cam device 71 transmitting a driving force F1 in driving by the contact of an input-side driving cam member 74 and an output member 75 (output-side driving cam member), and generating thrust in one axial direction, a second cam device 72 transmitting driven forces F2, F3 when driven by the contact of the output member 75 (input-side driven cam member integrated with output-side driving cam member) and an output-side driven cam member 76, and generating thrust in one axial direction, and a switching device 73 for switching the engagement of the first cam device 71 and a secondary movable sheave 63 (thrusted member to which generated thrust is transmitted), and the engagement of the second cam device 72 and the secondary movable sheave 63. The belt-type continuously variable transmission comprising the torque cam is also disclosed. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a torque cam device and a belt type continuously variable transmission.

  There are various torque cam devices. However, the input cam member is brought into contact with the drive cam surface formed on the output cam member, and the input cam member moves along the drive cam surface. Some perform torque transmission. In this torque cam device, both cam members are formed in a ring shape and the drive cam surface is formed in the circumferential direction, so that not only torque can be transmitted but also thrust can be generated in one of the axial directions. Some of them can be used, and such a torque cam device is used in a transmission of a vehicle, particularly a belt type continuously variable transmission.

  A torque cam device used in a belt-type continuously variable transmission is generally disposed between a secondary pulley and a final reduction gear, and transmits output torque as an engine output from the secondary pulley to the final reduction gear via both cam members. Will be. At this time, the thrust generated in one of the axial directions becomes the belt clamping pressure of the secondary pulley, and the belt can be clamped. Here, in the torque cam device of the belt type continuously variable transmission, a driven force is generated in addition to the driving force that is an output torque for moving the vehicle forward. This driven force is the same as the output torque in the direction opposite to the driving force transmitted from the secondary pulley side to reverse the vehicle, or the driving force transmitted from the final reduction gear side, for example, when using an engine brake. There is a resistance torque in the direction. For this reason, in a torque cam device used for a belt-type continuously variable transmission, it is necessary to transmit a driven force during driving via a cam roller in addition to the driving cam surface. Accordingly, the driven cam surface is formed in the circumferential direction on the output cam member. The driven cam surface is formed so as to be alternately arranged in the circumferential direction with the driving cam surface.

  In a torque cam device in which a driving cam surface and a driven cam surface are formed, when the driving state is switched from driving to driving or from driving to driving, the object to be contacted by the input cam member is driven. Switching from the cam surface to the driven cam surface or from the driven cam surface to the driving cam surface. When the drive state is switched, the input side cam member and the output side cam member rotate relative to each other in the circumferential direction, so that the input side cam member separates from one cam surface and contacts the other cam surface. Accordingly, there is a possibility that a time lag of torque transmission at the time of switching of the driving state occurs and impact torque is generated at the input side cam member and the output side cam member, and a shock occurs at the time of switching of the driving state.

  Conventionally, a torque cam device as shown in Patent Document 1 has been proposed. A conventional torque cam device disclosed in Patent Document 1 includes a first cam surface that contacts a cam roller and a cam member that is guided by a long groove and a pin so as to be movable only in the axial direction with respect to a cylindrical portion provided with the first cam surface. And a second cam surface provided on the cam member so as to be inclined in the direction opposite to the first cam surface and contacting the cam roller. This conventional torque cam device is used in a belt type continuously variable transmission.

  In this torque cam device, the cam roller is sandwiched between the first cam surface and the second cam surface by the compression force of the compression spring arranged in the axial direction. That is, the contact between the cam roller and the cam surface is not separated regardless of the driving state of the torque cam device. Therefore, in the conventional torque cam device, the contact between the cam roller and the cam surface is not separated regardless of the driving state of the torque cam device.

JP 63-210458 A

  However, in order to guide the cam member in the axial direction relative to the cylindrical portion, a sliding gap is formed in the circumferential direction between the long groove and the pin. That is, there is a backlash in the circumferential direction between the long groove and the pin. Further, when the conventional torque cam device transmits the driven force, a thrust in one direction of the axial direction is generated between the cam roller and the cam member. Here, the direction in which this thrust is generated is the same as the direction in which the compression spring is compressed. Therefore, when the generated thrust exceeds the compressive force of the compression spring, the compression spring is compressed, so that circumferential play occurs.

  Therefore, since it is necessary to close the generated play in the circumferential direction, there is a possibility that generation of a time lag of torque transmission at the time of switching of the driving state of the torque cam device cannot be suppressed.

  Therefore, the present invention has been made in view of the above, and provides a torque cam device and a belt-type continuously variable transmission that can suppress the occurrence of a time lag in torque transmission when the driving state is switched. It is for the purpose.

  In order to solve the above-described problems and achieve the object, the torque cam device according to the present invention includes an input-side drive cam member and an output-side drive cam member, and the input-side drive cam member and the output-side drive cam member. A first cam device that transmits a driving force during driving and generates a thrust force in one of the axial directions, an input driven cam member formed integrally with the output driving cam member, and It has an output driven cam member, and transmits a driven force during driving and a thrust in one of the axial directions by contact between the input driven cam member and the output driven cam member. Switching means for switching between engagement between the generated second cam device, the first cam device and the thrust member to which the generated thrust is transmitted, and engagement between the second cam device and the thrust member. When, Characterized in that it comprises.

  According to the present invention, in the torque cam device, the switching unit moves the input side drive cam member and the input side drive cam member by moving the input side drive cam member in one axial direction with respect to the thrust member. Drive-side engagement means for engaging with the thrust member, and the output-side driven cam member moving in one of axial directions with respect to the thrust member, the output-side driven cam member Driven-side engaging means for engaging the thrust member and the input-side driving cam member and the output-side driving cam member, and the input-side driving cam member is output to the output-side driving cam member. Driving-side pressing force generating means for pressing the input-side driving cam member in a direction in which the side-side driving cam member is moved in one of the axial directions; the input-side driven cam member; and the output-side driven cam Contact the member And the driven-side pushing member that presses the output-side driven cam member in a direction in which the output-side driven cam member is moved in one of the axial directions with respect to the input-side driven cam member. When permitting movement in one of the axial directions of any one of the pressure generating means and the input-side driving cam member or the output-side driven cam member, And a switching member that restricts movement.

  According to these inventions, when the engagement is switched by the switching device, the relative rotation of the first cam device or the second cam device is such that the input side drive cam member is relative to the output side drive cam member or the output side cover. When the drive cam member moves in one of the axial directions with respect to the input-side driven cam member, the input-side drive cam member moves relative to the output-side drive cam member or until the engagement is started. The output driven cam member rotates relative to the input driven cam member. Therefore, the relative rotation of the first cam device and the second cam device that occur when the driving state is switched is suppressed from the relative rotation when the driving state of the torque cam device having the cam surface opposed to the conventional circumferential direction is switched. Can do.

  Further, when the driving state is switched, the input side driven cam member and the output side driven cam member can move in one of the axial directions with respect to the thrust member by the generated thrust. The first cam device and the thrust member are engaged by the engaging means, or the second cam device and the thrust member are engaged by the driven side engaging means. When this engagement is performed, the width between the input side driving cam member and the output side driving cam member or the width between the output side driven cam member and the input side driven cam member does not change. Thereby, when the drive state is switched, the play in the circumferential direction does not occur in the first cam device or the second cam device.

  According to the present invention, in the torque cam device, the switching means engages the first cam device and the thrust member when there is no load.

  According to the present invention, when no load is applied, the first cam device and the thrust member are engaged by the driving side engaging means, and the second cam device and the thrust member by the driven engaging means are engaged. Don't join. Therefore, when the driving state is switched from the no-load state to the driving state, the first cam device and the thrust member are already engaged by the driving side engaging means, so that the first cam device rotates relatively. The driving force can be transmitted instantaneously. As a result, when this torque device is used in a belt-type continuously variable transmission, belt clamping pressure can be instantaneously generated, and the vehicle is not slacked when the vehicle is started and the belt clamping pressure that the torque cam device bears is insufficient. Can be suppressed.

  In the belt-type continuously variable transmission according to the present invention, at least two pulley shafts arranged in parallel and transmitting output torque from the drive source to one of the two pulley shafts are respectively provided on the two pulley shafts. Two pulleys comprising two movable sheaves sliding in the direction, two fixed sheaves facing the two movable sheaves in the axial direction, respectively, and transmission to any one of the two pulleys A belt that transmits the driving force from the drive source to the other pulley, and the torque cam device that generates a belt clamping pressure between the movable sheave and the fixed sheave.

  According to this invention, since the belt-type continuously variable transmission is configured using the torque cam device, it is possible to suppress occurrence of a time lag in torque transmission when the driving state is switched.

  In the torque cam device and the belt type continuously variable transmission according to the present invention, the engagement between the first cam device and the thrust member, which can always transmit the driving force by the switching means, is always driven by the switching means. Since the engagement between the second cam device and the thrust target member in a state where force transmission can be performed is switched, it is possible to suppress occurrence of a time lag in torque transmission when the driving state is switched. Play.

  Hereinafter, the present invention will be described in detail with reference to the drawings. In addition, this invention is not limited by the following Example. In addition, constituent elements in the following embodiments include those that can be easily assumed by those skilled in the art or that are substantially the same. Here, in the following embodiment, a case where the torque cam device according to the present invention is used for a belt type continuously variable transmission will be described. In the belt type continuously variable transmission, the torque cam device according to the present invention is used to generate a belt clamping pressure. An internal combustion engine (gasoline engine, diesel engine, LPG engine, etc.) is used as a drive source for generating a drive force transmitted to the belt type continuously variable transmission, but the invention is not limited to this. An electric motor may be used as a drive source.

  FIG. 1 is a skeleton diagram of a belt type continuously variable transmission including a torque cam device according to the present invention. FIG. 2 is a diagram illustrating the torque cam device at the time of no load and at the time of driving. FIG. 3A is a diagram illustrating the first cam device during no load and during driving. FIG. 3-2 is a diagram illustrating the second cam device during no load and during driving. FIG. 4 is a diagram illustrating a configuration example of the switching member. FIG. 5 is a diagram showing the torque cam device when driven. FIG. 6A is a diagram illustrating the first cam device when driven. FIG. 6B is a diagram illustrating the second cam device when driven. The driving force F1 in this embodiment is assumed to be generated clockwise when the torque cam device is viewed from the power transmission shaft side in FIGS. 3A is a sectional view taken along line BB in FIG. 2, FIG. 3B is a sectional view taken along line CC in FIG. 2, FIG. 6A is a sectional view taken along line DD in FIG. FIG. 5 is a cross-sectional view taken along line EE of FIG.

  As shown in FIG. 1, a transaxle 20 is disposed on the output side of the internal combustion engine 10. The transaxle 20 includes a transaxle housing 21, a transaxle case 22 attached to the transaxle housing 21, and a transaxle rear cover 23 attached to the transaxle case 22.

  A torque converter 30 is accommodated in the transaxle housing 21. On the other hand, inside the case constituted by the transaxle case 22 and the transaxle rear cover 23, a primary pulley 50 and a secondary pulley 60 which are two pulleys constituting the belt type continuously variable transmission 1 according to the present invention, and a primary A primary oil chamber 54 for generating belt clamping pressure in the pulley 50, a secondary oil chamber 64 for generating belt clamping pressure in the secondary pulley 60, the torque cam device 70 according to the present invention, and the belt 100 are housed. Reference numeral 40 denotes a forward / reverse switching mechanism, 80 denotes a final speed reducer that transmits the driving force of the internal combustion engine 10 to the wheels 110, and 90 denotes a power transmission path.

  As shown in FIG. 1, the torque converter 30 serving as a starting mechanism increases or transmits the output torque from the drive source, that is, the output torque from the internal combustion engine 10 to the belt type continuously variable transmission 1 as it is. The torque converter 30 includes at least a pump (pump impeller) 31, a turbine (turbine impeller) 32, a stator 33, a lockup clutch 34, and a damper device 35.

  The pump 31 is attached to a hollow shaft 36 that can rotate around the same axis as the crankshaft 11 of the internal combustion engine 10. That is, the pump 31 can rotate about the same axis as the crankshaft 11 together with the hollow shaft 36. The pump 31 is connected to the front cover 37. The front cover 37 is connected to the crankshaft 11 via the drive plate 12 of the internal combustion engine 10.

  The turbine 32 is disposed so as to face the pump 31. The turbine 32 is disposed inside the hollow shaft 36 and is attached to an input shaft 38 that can rotate about the same axis as the crankshaft 11. That is, the turbine 32 can rotate about the same axis as the crankshaft 11 together with the input shaft 38.

  A stator 33 is disposed between the pump 31 and the turbine 32 via a one-way clutch 39. The one-way clutch 39 is fixed to the transaxle housing 21. A lockup clutch 34 is disposed between the turbine 32 and the front cover 37, and the lockup clutch 34 is connected to an input shaft 38 via a damper device 35. The casing formed by the pump 31 and the front cover 37 is supplied with hydraulic oil as a hydraulic fluid from a hydraulic oil supply control device (not shown).

  Here, the operation of the torque converter 30 will be described. The output torque from the internal combustion engine 10 is transmitted from the crankshaft 11 to the front cover 37 via the drive plate 12. When the lock-up clutch 34 is released by the damper device 35, the output torque from the internal combustion engine 10 transmitted to the front cover 37 is transmitted to the pump 31 and circulates between the pump 31 and the turbine 32. It is transmitted to the turbine 32 via oil. The output torque from the internal combustion engine 10 transmitted to the turbine 32 is transmitted to the input shaft 38. That is, the torque converter 30 increases the output torque from the internal combustion engine 10 via the input shaft 38 and transmits it to the belt type continuously variable transmission 1 described later. In the above, the stator 33 can change the flow of hydraulic fluid circulating between the pump 31 and the turbine 32 to obtain a predetermined torque characteristic.

  On the other hand, when the lock-up clutch 34 is locked (engaged with the front cover 37) by the damper device 35, the output torque from the internal combustion engine 10 transmitted to the front cover 37 is directly not via hydraulic oil. It is transmitted to the input shaft 38. That is, the torque converter 30 transmits the output torque from the internal combustion engine 10 to the belt type continuously variable transmission 1 via the input shaft 38.

  An oil pump 26 is provided between the torque converter 30 and a forward / reverse switching mechanism 40 described later. The oil pump 26 includes a rotor 27, a hub 28, and a body 29. The oil pump 26 is connected to the pump 31 by a rotor 27 via a cylindrical hub 28. A body 29 is fixed to the transaxle case 22. The hub 28 is splined to the hollow shaft 36. Therefore, the oil pump 26 can be driven because the output torque from the internal combustion engine 10 is transmitted to the rotor 27 via the pump 31.

  As shown in FIG. 1, the forward / reverse switching mechanism 40 transmits the output torque from the internal combustion engine 10 transmitted through the torque converter 30 to the primary pulley 50 of the belt type continuously variable transmission 1. The forward / reverse switching mechanism 40 includes at least a planetary gear device 41, a forward clutch 42, and a reverse brake 43.

  The planetary gear device 41 includes a sun gear 44, a pinion 45, and a ring gear 46.

  The sun gear 44 is spline-fitted to a connecting member (not shown). This connecting member is spline-fitted to a primary pulley shaft 51 of a primary pulley 50 described later. Accordingly, the output torque from the internal combustion engine 10 transmitted to the sun gear 44 is transmitted to the primary pulley shaft 51.

  The pinion 45 meshes with the sun gear 44, and a plurality of (for example, three) pinions 45 are arranged around it. Each pinion 45 is held by a switching carrier 47 that supports the sun gear 44 so as to be integrally revolved. The switching carrier 47 is connected to the reverse brake 43 at its outer peripheral end.

  The ring gear 46 meshes with each pinion 45 held by the switching carrier 47 and is connected to the input shaft 38 of the torque converter 30 via the forward clutch 42.

  The forward clutch 42 is ON / OFF controlled by hydraulic oil supplied to a hollow portion (not shown) of the input shaft 38 from a hydraulic oil supply control device (not shown). When the forward clutch 42 is OFF, the output torque from the internal combustion engine 10 transmitted to the input shaft 38 is transmitted to the ring gear 46. On the other hand, when the forward clutch 42 is ON, the output torque from the internal combustion engine 10 transmitted to the input shaft 38 is directly transmitted to the sun gear 44 without the ring gear 46, the sun gear 44, and the pinions 45 rotating relative to each other.

  The reverse brake 43 is ON / OFF controlled by a brake piston (not shown) supplied with hydraulic oil from a hydraulic oil supply control device (not shown). When the reverse brake 43 is ON, the switching carrier 47 is fixed to the transaxle case 22 so that each pinion 45 cannot revolve around the sun gear 44. When the reverse brake 43 is OFF, the switching carrier 47 is released, and each pinion 45 can revolve around the sun gear 44.

  The primary pulley 50 of the belt-type continuously variable transmission 1 transmits the output torque from the internal combustion engine 10 transmitted through the forward / reverse switching mechanism 40 to the secondary pulley 60 by a belt 100 described later. As shown in FIG. 1, the primary pulley 50 includes a primary pulley shaft 51, a primary fixed sheave 52, a primary movable sheave 53, and a belt-type continuously variable transmission that generates belt clamping pressure on the primary pulley 50. And a primary oil chamber 54 that changes the transmission ratio of 1.

  The primary pulley shaft 51 is rotatably supported by bearings 101 and 102. Further, the primary pulley shaft 51 has a hydraulic oil passage (not shown) inside, and the hydraulic oil supplied from the hydraulic oil supply control device (not shown) to the primary oil chamber 54 flows into the hydraulic oil passage.

  The primary fixed sheave 52 is integrally provided on the outer periphery of the primary pulley shaft 51 so as to face the primary movable sheave 53. The primary movable sheave 53 is splined to the primary pulley shaft 51 so as to be slidable on the primary pulley shaft 51 in the axial direction. Between the primary fixed sheave 52 and the primary movable sheave 53, that is, between the surface of the primary fixed sheave 52 that faces the primary movable sheave 53 and the surface of the primary movable sheave 53 that faces the primary fixed sheave 52. A primary groove 100a having a shape is formed.

  The primary oil chamber 54 is configured by a back surface 53 a opposite to the surface facing the primary fixed sheave 52 of the primary movable sheave 53 and a disk-shaped primary partition wall 55 fixed to the primary pulley shaft 51. On the back surface 53a of the primary movable sheave 53, an annular protrusion 53b that protrudes in one axial direction, that is, protrudes toward the transaxle rear cover 23 is formed. On the other hand, the primary partition wall 55 is formed with an annular protrusion 55a that protrudes in the other axial direction, that is, toward the primary movable sheave 53 side. A seal member (not shown) such as a seal ring is provided between the protrusion 53b and the protrusion 55a. That is, the back surface 53a of the primary movable sheave 53 constituting the primary oil chamber 54 and the primary partition wall 55 are sealed by the seal member.

  The primary oil chamber 54 is supplied with hydraulic oil flowing into a hydraulic oil passage (not shown) of the secondary pulley shaft 61 through a hydraulic oil supply hole (not shown). That is, the hydraulic oil supply control device supplies hydraulic oil to the primary oil chamber 54, and the primary movable sheave 53 is slid in the axial direction by the pressure of the supplied hydraulic oil, so that the primary movable sheave 53 is primary fixed. It approaches or separates from the sheave 52. The primary oil chamber 54 generates a belt clamping pressure with respect to the belt 100 wound around the primary groove 100 a by applying an axial pressing force to the primary movable sheave 53 by the hydraulic oil supplied to the primary oil chamber 54. The axial position of the primary movable sheave 53 with respect to the primary fixed sheave 52 is changed. Thus, the primary oil chamber 54 has a function as a gear ratio changing means for changing the gear ratio of the belt type continuously variable transmission 1.

  The secondary pulley 60 of the belt type continuously variable transmission 1 transmits the output torque from the internal combustion engine 10 transmitted to the primary pulley 50 by the belt 100 to the final speed reducer 80 of the belt type continuously variable transmission 1. As shown in FIG. 1, the secondary pulley 60 includes a secondary pulley shaft 61, a secondary fixed sheave 62, a secondary movable sheave 63, and a secondary oil chamber 64 that generates belt clamping pressure on the secondary pulley 60. ing.

  As shown in FIG. 1, the secondary pulley shaft 61 is rotatably supported by bearings 103 and 104. A hydraulic oil passage (not shown) is formed between the secondary pulley shaft 61 and a power transmission shaft 91 disposed on the radially outer side of the secondary pulley shaft 61, and a hydraulic oil supply control (not shown) is provided in the hydraulic oil passage. The working oil that is the working fluid supplied from the apparatus to the secondary oil chamber 64 flows in.

  The secondary fixed sheave 62 is integrally provided on the outer periphery of the secondary pulley shaft 61 so as to face the secondary movable sheave 63. The secondary movable sheave 63 is a thrust member and is spline-fitted to the secondary pulley shaft 61 so as to be slidable on the secondary pulley shaft 61 in the axial direction. Between the secondary fixed sheave 62 and the secondary movable sheave 63, that is, between the surface of the secondary fixed sheave 62 facing the secondary movable sheave 63 and the surface of the secondary movable sheave 63 facing the secondary fixed sheave 62. A secondary groove 100b having a shape is formed. Reference numeral 66 denotes a parking brake gear.

  The secondary oil chamber 64 is formed between the secondary partition wall 65 and a back surface 63 a opposite to the surface facing the secondary fixed sheave 62 of the secondary movable sheave 63.

  The secondary partition wall 65 is a ring-shaped member and is rotatably supported by the secondary pulley shaft 61 by bearings 103 and 105. The secondary partition wall 65 is connected to the power transmission shaft 91 of the power transmission path 90. Here, the secondary partition wall 65 is restricted from moving relative to the secondary pulley shaft 61 in the axial direction. Therefore, the secondary partition wall 65 can rotate with respect to the secondary movable sheave 63, but the movement in the axial direction is restricted with respect to the secondary movable sheave 63. Further, the secondary partition wall 65 has a hydraulic oil supply hole for supplying hydraulic oil to the oil chamber 64 from a hydraulic oil passage (not shown) formed between the secondary pulley shaft 61 and the power transmission shaft 91 arranged on the radially outer side of the secondary pulley shaft 61. 65a is formed.

  Here, the secondary oil chamber 64 flows into a hydraulic oil passage (not shown) between the secondary pulley shaft 61 and the power transmission shaft 91 as shown by an arrow A in FIG. 2 via the hydraulic oil supply hole 65a. Hydraulic oil is supplied. In other words, the hydraulic oil supply control device supplies hydraulic oil to the secondary oil chamber 64, and the secondary movable sheave 63 is slid in the axial direction by the hydraulic pressure of the supplied hydraulic oil, so that the secondary movable sheave 63 is moved to the secondary fixed sheave. 62 is approached or separated. The secondary oil chamber 64 is a belt for the belt 100 wound around the secondary groove 100b by applying a pressing force in one of the axial directions to the secondary movable sheave 63 by the hydraulic oil supplied to the secondary oil chamber 64. It serves a part of the function of generating a pinching pressure and maintaining a constant contact radius of the belt 100 with respect to the primary pulley 50 and the secondary pulley 60.

  As shown in FIGS. 2 to 6-2, the torque cam device 70 includes a first cam device 71, a second cam device 72, and a switching device 73 as switching means.

  The first cam device 71 includes an input side drive cam member 74 and an output member 75 that is an output side drive cam member. The first cam device 71 transmits a driving force F1 to be described later, and generates thrust in one direction of the axial direction, that is, a direction in which the secondary movable sheave 63 is directed to the secondary fixed sheave 62.

  The input side drive cam member 74 is disposed between the back surface 63 a of the secondary movable sheave 63 and the output side drive cam portion 75 a of the output member 75. The input side drive cam member 74 is held by a drive side cam holding member 77 and an intermediate member 78. Therefore, the input side drive cam member 74 is supported between the drive side cam holding member 76 and the intermediate member 77 so as to be movable in the axial direction and rotatable in the circumferential direction. Here, the intermediate member 78 is positioned in one of the axial directions, i.e., secondary, by an elastic member 78a for positioning such as a spring disposed between the output side drive cam portion 75a and an input side driven cam portion 75c described later. It is pressed to the pulley side. That is, the positioning elastic member 78a performs positioning of the intermediate member 78 in the axial direction. The drive side cam holding member 77 is fixed to the output member 75 by a fixing means L such as a bolt.

  A drive cam surface 74a with which the drive-side cam roller 75b of the output member 75 contacts is formed at one end in the axial direction of the input-side drive cam member 74, here the end on the power transmission shaft side. A plurality of (for example, 3 to 4) drive cam surfaces 74 a are formed in the circumferential direction of the input side drive cam member 74. As shown in FIGS. 3A and 6-1, the drive cam surface 74a is an inclined surface that is inclined so as to rise in a direction opposite to the direction in which the secondary movable sheave 63 rotates by a drive force F1 described later. The shape and cam angle of the drive cam surface 74a are determined based on the magnitude of the driving force F1 transmitted by the first cam device 71, the magnitude of the thrust to be generated, and the like.

  The output member 75 is an output side drive cam member, and is a ring-shaped member having an L-shaped axial cross section, and is fixed to the secondary partition wall 65. Specifically, the radially inner end of the output member 75 is fixed to the radially outer end of the secondary partition wall 65. The output member 75 is rotatably supported by bearings 103 and 105 on the secondary pulley shaft 61 via the secondary partition wall 65. Accordingly, since the output member 75 is connected to the power transmission shaft 91 via the secondary partition wall 65, movement in the axial direction is restricted with respect to the input side drive cam member 74.

  This output member 75 is formed with an output side drive cam portion 75a that protrudes from the radially outer end toward the secondary pulley, and contacts the drive cam surface 74a of the input side drive cam member 74 at its tip. A cylindrical driving cam roller 75b is rotatably supported. A plurality (for example, 3 to 4) of drive side cam rollers 75b are formed in the circumferential direction of the output member 75 so as to face each of the drive cam surfaces 74a. The drive cam roller 75b is rotatably supported by the output drive cam portion 75a in order to reduce resistance when the input drive cam member 74 and the output member 75 are relatively rotated in the circumferential direction. The output side drive cam portion 75a may be fixed.

  As described above, the input-side drive cam member 74 is held by the drive-side cam holding member 77 and the intermediate member 78, and the output member 75 is fixed to the secondary partition 65 that is a rotating member different from the secondary movable sheave 63. So that it is connected to the power transmission shaft 91. Therefore, the input side drive cam member 74 and the output member 75 are supported so as to be relatively rotatable in the circumferential direction.

  By the relative rotation of the input side drive cam member 74 and the output member 75, the drive cam surface 74a of the input side drive cam member 74 and the drive side cam roller 75b of the output member 75 come into contact with each other. As a result, a driving force F1 described later is transmitted. Further, as shown in FIG. 3A, when the first cam device 71 transmits the driving force F1, the movement of the output member 75 in the axial direction with respect to the input side driving cam member 74 is restricted. Therefore, a driving side tooth clutch 73b, which will be described later, is engaged to generate a thrust in one of the axial directions.

  The second cam device 72 includes an output side driven cam member 76 and the output member 75 that is also an input side driven cam member. The second cam device 72 transmits driven forces F2 and F3, which will be described later, and generates thrust in one of the axial directions, that is, the direction in which the secondary movable sheave 63 is directed to the secondary fixed sheave 62. .

  The output side driven cam member 76 is disposed between the back surface 63 a of the secondary movable sheave 63 and the input side driven cam portion 75 c of the output member 75. That is, the output side driven cam member 76 is disposed on the radially inner side of the input side driving cam member 74. The output side driven cam member 76 is held by an intermediate member 78 and a driven side cam holding member 79. Accordingly, the output side driven cam member 76 is supported between the intermediate member 78 and the driven side cam holding member 79 so as to be movable in the axial direction and rotatable in the circumferential direction. Here, the driven cam holding member 79 is fixed to the output member 75 by fixing means L such as a bolt.

  A driven cam surface 76a with which the driven cam roller 75d of the output member 75 contacts is formed at one end in the axial direction of the output driven cam member 76, here the end on the power transmission shaft side. ing. A plurality of (for example, 3 to 4) driven cam surfaces 76 a are formed in the circumferential direction of the output side driven cam member 76. The driven cam surface 76a is formed so as to face the driving cam surface 74a of the first cam device 71 in the axial direction as shown in FIGS. 3-2 and 6-2, and is driven by a driving force F1 described later. It is an inclined surface which inclines so that the secondary movable sheave 63 may stand up in the direction of rotation. The shape and cam angle of the driven cam surface 76a are determined based on the magnitudes of the driven forces F2 and F3 transmitted by the second cam device 72, the magnitude of the thrust to be generated, and the like.

  The output member 75 is also an input side driven cam member. That is, the output member 75 functions as an output side driving cam member and an input side driven cam member. Accordingly, since the output member 75 is connected to the power transmission shaft 91 via the secondary partition wall 65, movement in the axial direction is restricted with respect to the output side driven cam member 76.

  The output member 75 is formed with an input driven cam portion 75c that protrudes from the radially inner end toward the secondary pulley, and a driven cam surface 76a of the output driven cam member 76 at the tip. A cylindrical driven cam roller 75d that is in contact with the roller is rotatably supported. A plurality of (for example, 3 to 4) driven cam rollers 75d are formed in the circumferential direction of the output member 75 so as to face each of the driven cam surfaces 76a. In this embodiment, the axis of the driven cam roller 75d and the axis of the driving cam roller 75b are located on one normal line of a circle centered on the center line OO. The driven cam roller 75d is rotatably supported by the input driven cam portion 75c in order to reduce resistance when the output driven cam member 76 and the output member 75 are relatively rotated in the circumferential direction. However, it may be fixed to the input side driven cam portion 75c.

  As described above, the output-side driven cam member 76 is held by the intermediate member 78 and the driven-side cam holding member 79, and the output member 75 is connected to the secondary partition wall 65 that is a rotating member different from the secondary movable sheave 63. It is connected to the power transmission shaft 91 by being fixed. Therefore, the output side driven cam member 76 and the output member 75 are supported so as to be relatively rotatable in the circumferential direction.

  As the output side driven cam member 76 and the output member 75 rotate relative to each other, the driven cam surface 76a of the output side driven cam member 76 and the driven side cam roller 75d of the output member 75 come into contact with each other. Driven forces F2 and F3, which will be described later, are transmitted by the two-cam device 72. As shown in FIG. 6B, when the second cam device 72 transmits the driven forces F2 and F3, the output member 75 moves in the axial direction with respect to the output side driven cam member 76. Since it is regulated, a driven side tooth clutch 73c, which will be described later, is engaged, so that thrust is generated in one of the axial directions.

  The switching device 73 includes an engagement between the first cam device 71 and the secondary movable sheave 63 that is a thrust member to which the thrust generated by the first cam device and the second cam device is transmitted, The engagement with the secondary movable sheave 63 is switched. The switching device 73 includes a switching member 73a, a driving side clutch 73b which is a driving side engaging means, a driven side clutch 73c which is a driven side engaging means, and a driving which is a driving side pressing force generating means. It is comprised by the side elastic member 73d and the driven side elastic member 73e which is a driven side pressing force generation means.

  As shown in FIG. 4, the switching member 73 a is a flat plate member, and a switching member rotating shaft 73 f is rotatably supported at the center in the longitudinal direction. An insertion hole 73h into which one end of the switching elastic member 73g is inserted is formed in the vicinity of one end in the longitudinal direction of the switching member 73a. The switching member 73a is rotatably supported between the secondary movable sheave 63 and the intermediate member 78.

  Here, a ring-shaped bearing member 63b is formed on the back surface 63a of the secondary movable sheave 63 so as to protrude toward the power transmission shaft. In the bearing member 63b, stepped portions 63c and 63c facing each other in the circumferential direction are formed at a plurality of circumferential locations (for example, 3 to 4 locations). Each step 63c is formed with a bearing 63d that supports the switching member rotating shaft 73f. Note that the back surface 63a of the secondary movable sheave 63 has a switching elastic member 73g at a position facing the insertion hole 73h of the switching member 73a when rotatably supported between the secondary movable sheave 63 and the intermediate member 78. An insertion hole 63e is formed in which the other end of the insertion hole is inserted.

  Further, at one end portion of the intermediate member 78, that is, the end portion on the secondary pulley side, projecting portions 78b and 78b facing in the circumferential direction are formed at a plurality of circumferential locations (for example, 3 to 4 locations). Yes. The distance between the projecting portions 78b and 78b facing in the circumferential direction is substantially the same as the distance between the step portions 63c and 63c facing in the circumferential direction. Each protrusion 78b is formed with a bearing 78c that supports the switching member rotating shaft 73f.

  The switching member 73 a is supported at both ends of the switching member rotating shaft 73 f by the bearing portions 63 d and 63 d of the secondary movable sheave 63 and the bearing portions 78 c and 78 c of the intermediate member 78. The switching member 73a is located between the driving side tooth clutch 73b and the driven side tooth clutch 73c, and as shown in FIG. 2, one side surface in the axial direction is the input side driving cam member 74 and the output side driven gear. The other side surface comes into contact with the back surface 63 a of the secondary movable sheave 63. That is, the switching member 73a rotates in any one of the rotation directions around the switching member rotation shaft 73f, so that either the input side driving cam member 74 or the output side driven cam member 76 is a shaft. Allow movement in one of the directions. At this time, when the switching member 73a allows movement in one of the axial directions of either the input-side driving cam member 74 or the output-side driven cam member 76, the switching member 73a It will restrict movement in one direction.

  Here, a switching elastic member 73g such as a spring is held between the insertion hole 73h of the switching member 73a and the insertion hole 63e of the back surface 63a of the secondary movable sheave 63. As shown in FIG. 2, the switching member 73 a has one direction in the rotational direction around the switching member rotation shaft 73 f, that is, one direction in the axial direction of the input-side drive cam member 74 by the switching elastic member 73 g. The output side driven cam member 76 is pressed in a direction that restricts movement in one of the axial directions.

  The drive-side tooth clutch 73 b is drive-side engagement means and engages the first cam device 71 and the secondary movable sheave 63. As shown in FIG. 3A and FIG. 6A, the drive side tooth clutch 73b includes a rear surface 63a of the secondary movable sheave 63 and the other end portion of the input side drive cam member 74, that is, an end portion on the secondary pulley side. Is formed between. Specifically, the drive-side tooth clutch 73 b includes a drive-side first claw portion (not shown) formed continuously in the circumferential direction on the back surface 63 a of the secondary movable sheave 63 and the other of the input-side drive cam member 74. It is comprised by the drive side 2nd nail | claw part which is formed in multiple numbers by the edge part continuously in the circumferential direction. The drive-side first claw portion (not shown) is in a direction opposite to the direction in which the driving force F1 acts on the secondary movable sheave 63 from the linear portion parallel to the axial direction and the end of the linear portion on the power transmission shaft side. And it is comprised by the inclination part which inclines toward the secondary pulley side. The drive-side second claw portion (not shown) has a linear portion parallel to the axial direction and a direction in which the driving force F1 acts on the secondary movable sheave 63 from the end portion on the secondary pulley side of the linear portion, and a power transmission shaft. It is comprised by the inclination part which inclines toward the edge part of the side.

  The drive-side tooth clutch 73b is configured such that the input-side drive cam member 74 moves in one axial direction relative to the secondary movable sheave 63, which is a thrust member, that is, toward the secondary pulley side. And the inclined portion of the second claw portion on the driving side are in contact with each other, the inclined portions slip, and the input-side driving cam member 74 moves toward the secondary pulley side with respect to the secondary movable sheave 63, while moving in the circumferential direction. Of these, it rotates in one direction, that is, the direction opposite to the direction in which the driving force F <b> 1 acts on the secondary movable sheave 63. As shown in FIG. 3A, the width between the back surface 63a of the secondary movable sheave 63 and the end portion on the secondary pulley side of the input side drive cam member 74 is narrowed to W1, and the drive side first claw portion. Of the first side claw and the second claw part of the driving side are engaged with each other, and the first claw part of the driving side and the second claw part of the driving side mesh with each other. Engagement takes place. Here, when the driving force F1 is applied to the torque cam device 70, the input side driving cam member 74 is rotated by the driving side tooth clutch 73b in the direction in which the driving force F1 is applied to the secondary movable sheave 63. The engagement by the drive side tooth clutch 73b is maintained.

  The driven-side tooth clutch 73 c is driven-side engaging means and engages the second cam device 72 and the secondary movable sheave 63. As shown in FIGS. 3-2 and 6-2, this driven side tooth clutch 73c is formed on the back surface 63a of the secondary movable sheave 63 and the other end of the output side driven cam member 76, that is, on the secondary pulley side. It is formed between the ends. Specifically, the driven-side tooth clutch 73c includes a plurality of driven-side first claw portions (not shown) continuously formed in the circumferential direction on the back surface 63a of the secondary movable sheave 63, and an output-side driven cam member 76. And a driven second claw portion (not shown) that is continuously formed in the circumferential direction on the other end portion of the second claw portion. The driven first claw portion (not shown) has a linear portion parallel to the axial direction and a direction in which the driving force F1 acts on the secondary movable sheave 63 from the end portion of the linear portion on the power transmission shaft side, and the secondary portion. It is comprised by the inclination part which inclines toward the pulley side. The second driven claw portion (not shown) is in a direction opposite to the direction in which the driving force F1 acts on the secondary movable sheave 63 from the linear portion parallel to the axial direction and the end portion of the linear portion on the secondary pulley side. And it is comprised by the inclination part which inclines toward the power transmission shaft side.

  The driven-side tooth clutch 73c moves in one of the axial directions with respect to the secondary movable sheave 63 that is a thrust member, that is, toward the secondary pulley side by moving the output-side driven cam member 76 to the driven pulley first clutch 73c. The inclined portion of the one claw portion and the inclined portion of the driven second claw portion come into contact with each other, and the inclined portions slide with each other, and the output driven cam member 76 moves to the secondary pulley side with respect to the secondary movable sheave 63. However, it rotates in the direction in which the driving force F1 acts on the secondary movable sheave 63 in the circumferential direction. As shown in FIG. 6B, the width between the back surface 63a of the secondary movable sheave 63 and the end on the secondary pulley side of the output driven cam member 76 is reduced to W4. When the linear part of the claw part and the linear part of the driven second claw part come into contact with each other, the driven first claw part and the driven second claw part mesh with each other, and the second cam device 72 and the secondary Engagement with the movable sheave 63 is performed. Here, when the driven forces F2 and F3 are applied to the torque cam device 70, the output driven cam member 76 is driven by the driven tooth clutch 73c in the direction in which the driving force F1 is applied to the secondary movable sheave 63. , That is, the direction in which the driven force F3 acts on the secondary movable sheave 63, or the direction in which the output member 75 acts on the secondary movable sheave 63, that is, the driven force F2 on the output member 75. Therefore, the engagement by the driven side tooth clutch 73c is maintained.

The driving side tooth clutch 73b and the driven side tooth clutch 73c are
When the switching member 73a is in a neutral position, that is, parallel to the radial direction of the secondary pulley 60, the driving side first claw portion and the driving side second claw portion are engaged, and the driven side first claw portion and the driven side are The length of each linear portion is set so that the second claw portion meshes with the second claw portion.

  The drive-side elastic member 73d is, for example, a spring and is drive-side pressing force generating means that presses the input-side drive cam member 74. The drive-side elastic member 73d includes a storage space portion 74b formed in the input-side drive cam member 74, and a storage space portion 77a (a two-dot chain line in FIG. 3A) formed in the drive-side cam holding member 77. Is housed between. Here, the storage space 74 b of the input side drive cam member 74 is formed along the drive cam surface 74 a, and at least one end 74 c is closed inside the input side drive cam member 74. The storage space 77 a of the driving cam holding member 77 is formed along the driving cam surface 74 a, and at least one end 77 b is closed inside the driving cam holding member 77.

  The drive side elastic member 73d is accommodated such that both ends thereof are in contact with one end 74c of the accommodation space 74b and one end 77b of the accommodation space 77a. Accordingly, the input side driving cam member 74 and the driving side cam holding member 77 are each subjected to the pressing force P1 in the direction in which the end portion 74c and the end portion 77b are separated by the driving side elastic member 73d. Here, the pressing force P1 generated by the drive side elastic member 73d is generated in a direction in which the input side drive cam member 74 and the drive side cam holding member 77 are separated along the drive cam surface 74a. Accordingly, the drive side elastic member 73d is in a direction in which the input side drive cam member 74 and the output member 75 that is the output side drive cam member are in contact with each other, and the input side drive cam member 74 is in contact with the output member 75. The input drive cam member 74 is pressed in one direction of the axial direction, that is, in the direction of movement toward the secondary pulley. Thereby, the contact between the input side drive cam member 74 and the output member 75 causes the input side drive cam member 74 to move even if the input side drive cam member 74 moves in the axial direction with respect to the output member 75. This is maintained because the contact between the drive cam surface 74a and the drive side cam roller 75b is maintained by the pressing force P1 that acts.

  The driven-side elastic member 73e is, for example, a spring, and is a driven-side pressing force generating unit that presses the output-side driven cam member 76. The driven elastic member 73e includes a storage space 76b formed in the output driven cam member 76 and a storage space 79a formed in the driven cam holding member 79 (two points in FIG. 6-2). It is housed in between. Here, the storage space 76 b of the output driven cam member 76 is formed along the driven cam surface 76 a, and at least one end 76 c is closed inside the output driven cam member 76. Yes. The storage space 79 a of the driven cam holding member 79 is formed along the driven cam surface 76 a, and at least one end 79 b is closed inside the driven cam holding member 79. .

  The driven-side elastic member 73e is accommodated such that both ends thereof are in contact with one end 76c of the accommodation space 76b and one end 79b of the accommodation space 79a. Accordingly, the output side driven cam member 76 and the driven side cam holding member 79 are each subjected to the pressing force P2 in the direction in which the end portion 76c and the end portion 79b are separated by the driven side elastic member 73e. . Here, the pressing force P2 generated by the driven elastic member 73e is generated in a direction in which the output driven cam member 76 and the driven cam holding member 79 are separated along the driven cam surface 76a. Accordingly, the driven-side elastic member 73e is in a direction in which the output-side driven cam member 76 and the output member 75 that is the input-side driven cam member are in contact with each other, and the output-side driven cam member 76 is connected to the output member. The output driven cam member 76 is pressed in one of the axial directions with respect to 75, that is, in the direction of moving toward the secondary pulley. Thereby, the contact between the output side driven cam member 76 and the output member 75 is performed even if the output side driven cam member 76 moves in the axial direction with respect to the output member 75. This is maintained because the contact between the driven cam surface 76a and the driven cam roller 75d is maintained by the pressing force P2 acting on the member 76.

  A power transmission path 90 is disposed between the secondary pulley 60 and the final reduction gear 80. The power transmission path 90 includes a power transmission shaft 91 and an intermediate shaft 92 parallel to the secondary pulley shaft 61, a counter drive pinion 93, a counter driven gear 94, and a final drive pinion 95. The power transmission shaft 91 is rotatably supported by bearings 106 and 107 via the secondary partition wall 65 and the output member 75. The intermediate shaft 92 is rotatably supported by bearings 108 and 109. The counter drive pinion 93 is fixed to the power transmission shaft 91. The counter driven gear 94 is fixed to the intermediate shaft 92 and meshed with the counter drive pinion 93. Further, the final drive pinion 95 is fixed to the intermediate shaft 92.

  The final reduction gear 80 of the belt-type continuously variable transmission 1 transmits the output torque from the internal combustion engine 10 transmitted through the power transmission path 90 from the wheels 110 and 110 to the road surface. The final reduction gear 80 includes a differential case 81 having a hollow portion, a pinion shaft 82, differential pinions 83 and 84, and side gears 85 and 86.

  The differential case 81 is rotatably supported by bearings 87 and 88. A ring gear 89 is provided on the outer periphery of the differential case 81, and the ring gear 89 is engaged with the final drive pinion 95. The pinion shaft 82 is attached to the hollow portion of the differential case 81. The differential pinions 83 and 84 are rotatably attached to the pinion shaft 82. The side gears 85 and 86 are meshed with both of the differential pinions 83 and 84. The side gears 85 and 86 are fixed to the drive shafts 111 and 112, respectively.

  The drive shafts 111 and 112 have side gears 85 and 86 fixed to one end thereof, respectively, and wheels 110 and 110 are attached to the other end thereof.

  The belt 100 of the belt type continuously variable transmission 1 transmits the output torque from the internal combustion engine 10 transmitted via the primary pulley 50 to the secondary pulley 60. As shown in FIG. 1, the belt 100 is wound around a primary groove 100 a of the primary pulley 50 and a secondary groove 100 b of the secondary pulley 60. The belt 100 is an endless belt composed of a number of metal pieces and a plurality of steel rings.

  Next, the operation of the belt type continuously variable transmission 1 including the torque cam device 70 according to the present invention will be described. First, general forward and reverse travel of the vehicle will be described. When a driver selects a forward position by a shift position device (not shown) provided in the vehicle, an ECU (Engine Control Unit) (not shown) is operated by a forward clutch 42 by hydraulic oil supplied from a hydraulic oil supply control device (not shown). Is turned on, the reverse brake 43 is turned off, and the forward / reverse switching mechanism 40 is controlled. As a result, the input shaft 38 and the primary pulley shaft 51 are directly connected. That is, the sun gear 44 and the ring gear 46 of the planetary gear device 41 are directly connected, the primary pulley shaft 51 is rotated in the same direction as the rotation direction of the crankshaft 11 of the internal combustion engine 10, and the output torque from the internal combustion engine 10 is converted to the primary pulley. 50. The output torque from the internal combustion engine 10 transmitted to the primary pulley 50 is transmitted to the secondary pulley 60 via the belt 100 and rotates the secondary pulley shaft 61 of the secondary pulley 60.

  The output torque of the internal combustion engine 10 transmitted to the secondary pulley 60 is transmitted to the torque cam device 70. The output torque transmitted to the torque cam device 70 is transmitted to the power transmission shaft 91 of the power transmission path 90. The output torque transmitted to the power transmission shaft 91 is transmitted to the intermediate shaft 92 via the counter drive pinion 93 and the counter driven gear 94, and rotates the intermediate shaft 92. The output torque transmitted to the intermediate shaft 92 is transmitted to the differential case 81 of the final reduction gear 80 via the final drive pinion 95 and the ring gear 89, and the differential case 81 is rotated. The output torque from the internal combustion engine 10 transmitted to the differential case 81 is transmitted to the drive shafts 111 and 112 via the differential pinions 83 and 84 and the side gears 85 and 86, and to the wheels 110 and 110 attached to the ends thereof. Then, the wheels 110 and 110 are rotated, and the vehicle moves forward.

  On the other hand, when the driver selects the reverse position by a shift position device (not shown) provided in the vehicle, the ECU (not shown) turns off the forward clutch 42 with the hydraulic oil supplied from the hydraulic oil supply control device (not shown). The reverse brake 43 is turned on and the forward / reverse switching mechanism 40 is controlled. As a result, the switching carrier 47 of the planetary gear unit 41 is fixed to the transaxle case 22 and is held by the switching carrier 47 so that each pinion 45 only rotates. Accordingly, the ring gear 46 rotates in the same direction as the input shaft 38, and each pinion 45 that meshes with the ring gear 46 also rotates in the same direction as the input shaft 38, and the sun gear 44 that meshes with each pinion 45 moves to the input shaft 38. And rotate in the opposite direction. That is, the primary pulley shaft 51 connected to the sun gear 44 rotates in the direction opposite to the input shaft 38. Thereby, the secondary pulley shaft 61 of the secondary pulley 60 rotates in the opposite direction to the case where the driver selects the forward position.

  The output torque of the internal combustion engine 10 transmitted to the secondary pulley 60 is transmitted to the torque cam device 70. The output torque transmitted to the torque cam device 70 is transmitted to the power transmission shaft 91 of the power transmission path 90, and the power transmission shaft 91 rotates in the opposite direction to the case where the driver selects the forward position. Then, the intermediate shaft 92, the differential case 81, the drive shafts 111, 112, and the like rotate in the opposite direction to the case where the driver selects the forward position, and the vehicle moves backward.

  The ECU (not shown) includes various conditions such as the vehicle speed and the driver's accelerator opening, and a map (for example, an optimal fuel consumption curve based on the engine speed and the throttle opening) stored in the storage unit of the ECU. Based on the above, the gear ratio of the belt-type continuously variable transmission 1 is controlled so that the operating state of the internal combustion engine 10 is optimized. The control of the gear ratio of the belt type continuously variable transmission 1 includes changing the gear ratio and fixing the gear ratio (gear ratio γ steady). The change of the gear ratio and the fixing of the gear ratio are performed by controlling the hydraulic pressure of hydraulic oil supplied from a hydraulic oil supply control device (not shown) to the primary oil chamber 54 that generates belt clamping pressure in the primary pulley 50. The change of the gear ratio is mainly performed by adjusting the distance between the primary fixed sheave 52 and the primary movable sheave 53, that is, the width of the primary groove 100a, by sliding the primary movable sheave 53 in the axial direction of the primary pulley shaft 51. Is done. As a result, the contact radius of the belt 100 in the primary pulley 50 changes, and the speed ratio, which is the ratio between the rotation speed of the primary pulley 50 and the rotation speed of the secondary pulley 60, is controlled steplessly (continuously).

  For example, when a large torque is not required when the vehicle is traveling at a high speed, the primary movable sheave 53 is adjusted closest to the primary fixed sheave 52, that is, adjusted so that the width of the primary groove 100a is minimized. Thereby, the contact radius of the belt 100 in the primary pulley 50 is maximized, the contact radius of the belt 100 in the secondary pulley 60 is minimized, and the speed ratio is minimized. Here, since the width between the secondary fixed sheave 62 and the secondary movable sheave 63 is maximized, the distance between the secondary movable sheave 63 and the output member 75 is minimized.

  When a large torque is required at the time of starting the vehicle, etc., the primary movable sheave 53 is adjusted so as to be farthest from the primary fixed sheave 52, that is, the width of the primary groove 100a is maximized. As a result, the contact radius of the belt 100 in the primary pulley 50 is minimized, the contact radius of the belt 100 in the secondary pulley 60 is maximized, and the speed ratio is maximized. Here, since the width between the secondary fixed sheave 62 and the secondary movable sheave 63 is minimized, the width between the secondary movable sheave 63 and the output member 75 is maximized.

  On the other hand, in the secondary pulley 60, the torque of the hydraulic oil supplied from a hydraulic oil supply control device (not shown) to the secondary oil chamber 64 that is a belt clamping pressure generating unit is controlled by the torque cam device 70 to the secondary movable sheave 63. The belt clamping pressure for clamping the belt 100 generated between the secondary fixed sheave 62 and the secondary movable sheave 63 is adjusted by thrust in one direction of the generated axial direction. As a result, the tension of the belt 100 wound between the primary pulley 50 and the secondary pulley 60 is controlled.

  Next, the operation of the torque cam device 70 will be described. Here, the driving force F1 during driving refers to a unidirectional force transmitted to the thrust member. When the torque cam device 70 is used in the belt-type continuously variable transmission 1, it means the output torque of the internal combustion engine 10 in the direction in which the vehicle is transmitted to the secondary movable sheave 63 of the torque cam device 70 via the belt 100. On the other hand, the driven force F2 at the time of driven means a force in the same direction as the driving force F1 at the time of driving transmitted from a member integrated with the output member 75 which is an input side driven cam member. The driven force F3 refers to the force in the other direction transmitted to the thrust member. When the torque cam device 70 is used in the belt-type continuously variable transmission 1, the output torque of the internal combustion engine 10 in the direction in which the vehicle transmitted to the secondary movable sheave 63 of the torque cam device 70 via the belt 100 is moved backward, This refers to the resistance torque transmitted to the output member 75 when the brake is used.

  First, the torque cam device 70 at the time of no load will be described. When no load is applied, neither the driving force F1 nor the driven forces F2 and F3 are applied to the torque cam device 70. In this case, as shown in FIGS. 3A and 3B, the force acting on the torque cam device 70 is generated by the drive side elastic member 73d by the output side drive cam member 74 and the output side drive cam member. , A pressing force P2 acting on the output-side driven cam member 76 and the output member 75 by the driven-side elastic member 73e, and a switching member rotation acting on the switching member 73a by the switching elastic member 73g The movement in one direction among the rotation directions around the shaft 73f, that is, the one direction in the axial direction of the input side driving cam member 74 is allowed, and the one direction in the axial direction of the output side driven cam member 76 is allowed. This is the pressing force in the direction of restricting movement.

  Therefore, the switching member 73a tries to rotate in one of the rotation directions by the pressing force of the switching elastic member 73g and the pressing force P1 acting on the input side drive cam member 74, and is in contact with the switching member 73a. The output-side driven cam member 76 maintains contact with the output member 75 that is the input-side driven cam member (contact between the driven-side cam roller 75d and the driven cam surface 76a) against the pressing force P2. In this state, the output member 75 moves to the other direction of the axial direction, that is, to the power transmission shaft side. As shown in FIG. 3B, the width between the back surface 63a of the secondary movable sheave 63 and the end of the output driven cam member 76 on the secondary pulley side is the straight line of the driven first claw portion. And the driven-side second claw portion are not in contact with each other, and the driven-side first claw portion and the driven-side second claw portion have a width W2 that does not mesh with each other. The second cam device 72 and the secondary movable sheave 63 are not engaged by the scratch 73c.

  On the other hand, the switching member 73a tries to rotate in one of the rotational directions by the pressing force of the switching elastic member 73g, so that the input side driving cam member 74 is pressed by the pressing force P1 applied by the driving side elastic member 73d. In a state where contact with the output member 75 that is the output side drive cam member (contact between the drive cam surface 74a and the drive side cam roller 75b) is maintained, one direction of the axial direction with respect to the output member 75, that is, Move to the secondary pulley side. As shown in FIG. 3A, the width between the back surface 63a of the secondary movable sheave 63 and the end portion on the secondary pulley side of the input side drive cam member 74 is equal to the linear portion of the drive side first claw portion. The first cam device 71 by the drive-side tooth clutch 73b has a width W1 which is a width where the drive-side first claw portion and the drive-side second claw portion mesh with each other. And the secondary movable sheave 63 are engaged.

  That is, in the torque cam device 70 when there is no load, the input side drive cam member 74 and the output side drive cam member 74 are in contact with each other, and the output side driven cam member 76 and the input side driven cam member. The output member 75 is in contact with the output member 75. In addition, in the torque cam device 70 at the time of no load, the first cam device 71 and the secondary movable sheave 63 that is the thrust member are engaged by the drive side tooth clutch 73b.

  Next, the torque cam device 70 when the driving state shifts from no load to driving will be described. As shown in FIGS. 3A and 3B, when the torque cam device 70 is switched from the no-load time to the driving time, the driving force F <b> 1 that is the output torque of the internal combustion engine 10 in the direction in which the vehicle moves forward is transmitted via the belt 100. It is transmitted to the secondary movable sheave 63. Here, as described above, since the first cam device 71 and the secondary movable sheave 63 are engaged with each other by the drive side toothed clutch 73b when there is no load, the input side drive cam is driven from the secondary movable sheave 63. The driving force F1 is instantaneously transmitted to the member 74 via the driving side clutch 73b. On the other hand, as described above, when no load is applied, the second cam device 72 and the secondary movable sheave 63 are not engaged with each other by the driven side tooth clutch 73c. The driving force F1 is not transmitted to the cam member 76 via the driven-side tooth clutch 73c.

  The contact between the drive cam surface 74a and the drive side cam roller 75b at no load is always maintained by the drive side elastic member 73d regardless of the width between the secondary movable sheave 63 and the secondary fixed sheave 62. The driving force F1 transmitted to the side drive cam member 74 is instantaneously transmitted to the output member 75 as the output side drive cam member via the drive cam surface 74a and the drive side cam roller 75b. That is, relative rotation does not occur between the input side drive cam member 74 and the output member 75, and the internal combustion engine 10 in the direction in which the vehicle moves forward between the input side drive cam member 74 and the output member 75. Output torque is transmitted instantaneously. Thereby, the first cam device 71 can transmit the driving force F <b> 1 transmitted to the secondary movable sheave 63 to the power transmission shaft 91.

  Further, the driving force F1 transmitted from the input side driving cam member 74 to the output member 75 causes the input side driving cam member 74 to move in one of the axial directions, that is, to the secondary pulley side with respect to the output member 75. The thrust which is the force to generate is generated. That is, the first cam device 71 can instantaneously transmit the driving force F1 when the switching from the no load to the driving is performed, and can generate the axial thrust instantaneously. This thrust acts on the secondary movable sheave 63 as a force in a direction in which the secondary movable sheave 63 is directed toward the secondary fixed sheave 62, and a belt clamping pressure for clamping the belt 100 between the secondary movable sheave 63 and the secondary fixed sheave 62 is generated. appear.

  As described above, when the torque cam device 70 is switched from no load to driving when the vehicle is started, the first cam device 71 can instantaneously transmit the driving force F1 without relative rotation. The clamping pressure can be generated instantaneously. Accordingly, it is possible to suppress the occurrence of a time lag in torque transmission and the occurrence of shock when the vehicle starts. Further, the shortage of the belt clamping pressure borne by the torque cam device 70 can be suppressed.

  Next, the torque cam device 70 when the driving state is switched from no load to driven is described. Specifically, from when there is no load, when the output torque of the internal combustion engine 10 in the direction in which the vehicle moves backward is transferred to the secondary movable sheave 63 as the driven force F3 in the direction opposite to the driving force F1, the driving is switched. The torque cam device 70 will be described. As shown in FIGS. 6A and 6B, when the torque cam device 70 is switched from the no-load state to the driven state, the driven force F3, which is the output torque of the internal combustion engine 10 in the direction of moving the vehicle backward, causes the belt 100 to move. To the secondary movable sheave 63. Here, as described above, when there is no load, the first cam device 71 and the secondary movable sheave 63 are engaged with each other by the driving side clutch 73b, but the driven force F3 is the driving force F1. Therefore, the engagement between the first cam device 71 and the secondary movable sheave 63 by the drive side toothed clutch 73b cannot be maintained.

  And the pressing force P1 which acts when the inclination part of the drive side 1st claw part of the drive side tooth clutch 73b and the inclination part of the drive side 2nd claw part slide in the direction opposite to the direction which slides when engaging. The input side drive cam member 74 moves against the secondary movable sheave 63 in the other axial direction, that is, toward the power transmission shaft side. Thus, the force acting on the switching member 73a becomes the pressing force by the switching elastic member 73g and the pressing force P2 acting via the output-side driven cam member 76 in contact with the switching member 73a. Here, in the switching elastic member 73g, the driving side elastic member 73d and the driven side elastic member 73e, the switching elastic member 73g is generated more in the axial direction than the driving side elastic member 73d and the driven side elastic member 73e. The pressing force is set to be small. Accordingly, the driven force elastic member 73e opposes the pressing force of the switching elastic member 73g and moves the output side driven cam member 76 in one of the axial directions with respect to the output member 75, that is, toward the secondary pulley. While moving, the switching member 73a is rotated in the other direction among the rotation directions. The output driven cam member 76 is also applied with the pressing force P2 by the driven elastic member 73e even when moving in one of the axial directions with respect to the output member 75. The contact with the output member 75 that is the side driven cam member (contact between the driven cam surface 76a and the driven cam roller 75d) is maintained.

  When the switching member 73a rotates in the other direction of the rotation direction to reach the neutral position, the engagement of the driven-side first claw portion and the driven-side second claw portion of the driven-side tooth clutch 73c is started. That is, the engagement between the second cam device 72 and the secondary movable sheave 63 by the driven side tooth clutch 73c is started. Here, the driven force F3 is transmitted from the secondary movable sheave 63 to the output side driven cam member 76 via the driven side clutch 73c. Due to the driven force F3 transmitted from the output-side driven cam member 76 to the output member 75, the output-side driven cam member 76 moves in one axial direction relative to the output member 75, that is, toward the secondary pulley. Thrust that is the force to move is generated. With this generated thrust, the output side driven cam member 76 is further moved in one axial direction relative to the output member 75, that is, the secondary pulley side, and the switching member 73a is further moved in the other direction in the rotational direction. Rotate. As a result, the driven-side first claw portion and the driven-side second claw portion of the driven-side tooth clutch 73c are engaged with each other, and the second cam device 72 and the secondary movable sheave 63 are engaged by the driven-side tooth clutch 73c. Is done.

  At this time, as shown in FIG. 6A, the width between the back surface 63a of the secondary movable sheave 63 and the end portion on the secondary pulley side of the input side drive cam member 74 is the straight portion of the drive side first claw portion. And the straight portion of the driving side second claw portion do not contact each other, and the driving side first claw portion and the driving side second claw portion have a width W3 that does not mesh with each other. The cam device 71 and the secondary movable sheave 63 are not engaged. Therefore, the driven force F3 is not transmitted from the secondary movable sheave 63 to the input-side drive cam member 74 via the drive-side tooth clutch 73b.

  The contact between the driven cam surface 76a and the driven cam roller 75d during no load is always maintained by the driven elastic member 73e regardless of the width between the secondary movable sheave 63 and the secondary fixed sheave 62. Therefore, the driven force F3 transmitted to the output side driven cam member 76 is transmitted to the output member 75 that is the input side driven cam member via the driven cam surface 76a and the driven side cam roller 75d.

  Further, due to the driven force F3 transmitted from the output side driven cam member 76 to the output member 75, the output side driven cam member 76 is in one of the axial directions with respect to the output member 75, that is, on the secondary pulley side. Thrust, which is the force that tries to move to, is generated. That is, the second cam device 72 can transmit the driven force F3 and generate axial thrust when switching from no load to driven. This thrust acts on the secondary movable sheave 63 as a force in a direction in which the secondary movable sheave 63 is directed toward the secondary fixed sheave 62, and a belt clamping pressure for clamping the belt 100 between the secondary movable sheave 63 and the secondary fixed sheave 62 is generated. appear.

  Next, the torque cam device 70 when the driving state is switched from driving to driven is described. Specifically, the resistance torque transmitted to the power transmission shaft 91 from the time of driving when the driving force F1 is transmitted to the secondary movable sheave 63 is input-side driven as the driven force F2 in the same direction as the driving force F1. The torque cam device 70 at the time of switching when driven is transmitted to the output member 75 which is a cam member will be described. The driven force F2 transmitted to the output 75 is transmitted to the input side driving cam member 74 via the driving cam surface 74a and the driving side cam roller 75b. Further, the contact between the driven cam surface 76a and the driven cam roller 75d during driving is always maintained by the driven elastic member 73e regardless of the width between the secondary movable sheave 63 and the secondary fixed sheave 62. Therefore, the driven force F2 transmitted to the output member 75 is transmitted to the output driven cam member 76 via the driven cam surface 76a and the driven cam roller 75d.

  Here, at the time of driving, as shown in FIGS. 3A and 3B, the first cam device 71 and the secondary movable sheave 63 are engaged by the driving side toothed clutch 73b, and the driven side two clutching is performed. The second cam device 72 and the secondary movable sheave 63 are not engaged by the scratch 73c. Since the driven force F2 acts on the input side drive cam member 74 in the same direction as the drive force F1, the engagement between the first cam device 71 and the secondary movable sheave 63 by the drive side tooth clutch 73b cannot be maintained. Therefore, the pressing force P1 acting when the inclined portion of the driving side first claw portion and the inclined portion of the driving side second claw portion of the driving side tooth clutch 73b slide in the direction opposite to the sliding direction when engaged. The input side drive cam member 74 moves against the secondary movable sheave 63 in the other direction in the axial direction. The driven force elastic member 73e moves the output driven cam member 76 in one of the axial directions with respect to the output member 75 against the pressing force of the switching elastic member 73g. The member 73a is rotated in the other direction among the rotation directions. The output driven cam member 76 is also applied with the pressing force P2 by the driven elastic member 73e even when moving in one of the axial directions with respect to the output member 75. The contact with the output member 75 that is the side driven cam member (contact between the driven cam surface 76a and the driven cam roller 75d) is maintained.

  When the switching member 73a rotates in the other direction of the rotation direction to reach the neutral position, the engagement between the second cam device 72 and the secondary movable sheave 63 by the driven side tooth clutch 73c is started, and the output side driven cam member The driven force F2 is transmitted from 76 to the secondary movable sheave 63 via the driven-side tooth clutch 73c. At this time, due to the driven force F <b> 2 transmitted from the output member 75 to the output side driven cam member 76, thrust in one direction of the axial direction is generated in the output side driven cam member 76. With this generated thrust, the output side driven cam member 76 is moved in one of the axial directions with respect to the output member 75, and the switching member 73a is further rotated in the other direction of the rotational direction. Thereby, engagement with the 2nd cam apparatus 72 and the secondary movable sheave 63 by the driven side tooth clutch 73c is performed. As a result, the driven force F2 transmitted from the output member 75 to the output side driven cam member 76 via the driven cam surface 76a and the driven side cam roller 75d is secondary via the driven side tooth clutch 73c. It is transmitted to the movable sheave 63.

  At this time, as shown in FIG. 6A, the engagement between the first cam device 71 and the secondary movable sheave 63 by the drive side tooth clutch 73b is not performed. The driven force F2 is not transmitted via the drive side tooth clutch 73b.

  As described above, the second cam device 72 can transmit the driven force F2 and generate axial thrust when switching from driving to driven. This thrust acts on the secondary movable sheave 63 as a force in a direction in which the secondary movable sheave 63 is directed toward the secondary fixed sheave 62, and a belt clamping pressure for clamping the belt 100 between the secondary movable sheave 63 and the secondary fixed sheave 62 is generated. appear.

  Here, the output side driven cam member when the engagement is switched from the engagement of the first cam device 71 and the secondary movable sheave 63 to the engagement of the second cam device 72 and the secondary movable sheave 63 by the switching device 73. The relative rotation between the output member 75 and the output-side driven cam member 76 is such that the output-side driven cam member 76 moves in one of the axial directions with respect to the output member 75, whereby the rear surface 63 a of the secondary movable sheave 63 and the output side The output-side driven cam member 76 rotates relative to the output member 75 until the width between the driven cam member 76 and the end on the secondary pulley side becomes W2 to W4. This relative rotation is smaller than the relative rotation when a torque cam device having a cam surface opposed to the conventional circumferential direction is switched from driving to driving. Therefore, the relative rotation between the output member 75, which is an input-side driven cam member, and the output-side driven cam member 76 that occurs when the torque cam device 70 is switched from driving to driving can be suppressed.

  Next, the torque cam device 70 when the driving state is switched from the driven state to the driving state will be described. Specifically, the resistance torque transmitted to the power transmission shaft 91 is transmitted as the driven force F2 in the same direction as the driving force F1 to the output member 75 that is the input side driven cam member from the driven state to the secondary state. The torque cam device 70 at the time of switching when the driving force F1 is transmitted to the movable sheave 63 will be described. In the driven state, as shown in FIGS. 6A and 6B, the second cam device 72 and the secondary movable sheave 63 are engaged with each other by the driven side tooth clutch 73c, and the driving side tooth clutch 73b. The first cam device 71 and the secondary movable sheave 63 are not engaged with each other. Since the driving force F1 acts on the secondary movable sheave 63, the engagement between the second cam device 72 and the secondary movable sheave 63 by the driven side tooth clutch 73c cannot be maintained.

  Therefore, the inclined portion of the driven-side first claw portion and the inclined portion of the driven-side second claw portion of the driven-side tooth clutch 73c act by sliding in the opposite direction to the sliding direction when engaged. The output side driven cam member 76 moves in the other direction of the axial direction with respect to the secondary movable sheave 63 against the pressing force P2. The drive force elastic member 73d moves the input side drive cam member 74 in one of the axial directions with respect to the output member 75 against the pressing force of the switching elastic member 73g, and also switches the switching member 73a. Is rotated in one of the rotation directions. The input side drive cam member 74 is also driven by the output side drive because the pressing force P1 is applied by the drive side elastic member 73d when moving in one of the axial directions with respect to the output member 75. Contact with the output member 75, which is a cam member (contact between the drive cam surface 74a and the drive cam roller 75b), is maintained.

  When the switching member 73a rotates in one of the rotational directions to reach the neutral position, the engagement of the first cam device 71 and the secondary movable sheave 63 by the drive side tooth clutch 73b is started, and the input side drive cam member 74 starts the secondary operation. A driving force F1 is transmitted to the movable sheave 63 via the driving side clutch 73b. At this time, the driving force F <b> 1 transmitted from the input side drive cam member 74 to the output member 75 generates a thrust force in one direction of the axial direction on the input side drive cam member 74. With this generated thrust, the input side drive cam member 74 is moved in one of the axial directions with respect to the output member 75, and the switching member 73a is further rotated in one of the rotational directions. Thereby, engagement with the 1st cam apparatus 71 and the secondary movable sheave 63 by the drive side tooth clutch 73b is performed. Thus, the driving force F1 transmitted from the input side driving cam member 74 to the output member 75 via the driving cam surface 74a and the driving side cam roller 75b is transmitted to the secondary movable sheave 63 via the driving side tooth clutch 73b. Is done.

  At this time, as shown in FIG. 3-2, the second driven sheave 63 and the secondary movable sheave 63 are not engaged with each other by the driven side toothed clutch 73c. No driving force F1 is transmitted to 76 via the driven-side tooth clutch 73c.

  As described above, the first cam device 71 can transmit the driving force F1 and can generate axial thrust when switching from driven to driven. This thrust acts on the secondary movable sheave 63 as a force in a direction in which the secondary movable sheave 63 is directed toward the secondary fixed sheave 62, and a belt clamping pressure for clamping the belt 100 between the secondary movable sheave 63 and the secondary fixed sheave 62 is generated. appear.

  Here, the input side drive cam member when the engagement is switched from the engagement of the second cam device 72 and the secondary movable sheave 63 to the engagement of the first cam device 71 and the secondary movable sheave 63 by the switching device 73. The relative rotation between the output member 75 and the input drive cam member 74 is such that the input drive cam member 74 moves in one of the axial directions with respect to the output member 75, and the back surface 63 a of the secondary movable sheave 63 and the input drive. The input side drive cam member 74 is rotated relative to the output member 75 until the width between the end of the cam member 74 on the secondary pulley side becomes W1 to W1. This relative rotation is smaller than the relative rotation when a torque cam device having a cam surface facing in the circumferential direction is switched from driven to driven. Therefore, it is possible to suppress relative rotation between the input side drive cam member 74 and the output side drive cam member, which is generated when the torque cam device 70 is switched from driven to driven.

  Thus, the torque cam device 70 can suppress the relative rotation that occurs in the first cam device and the second cam device when the drive state is switched. Thereby, generation | occurrence | production of the time lag of the transmission of torque at the time of switching can be suppressed. Further, the torque cam device 70 is engaged with the first cam device 71 and the secondary movable sheave 63 by the driving-side tooth clutch 73b or second by the driven-side tooth clutch 73c by the generated thrust when the driving state is switched. When the cam device 72 and the secondary movable sheave 63 are engaged, the widths between the input-side drive cam member 74 and the output-side driven cam member 76 and the output member 75 do not change, so There is no play. Therefore, unlike the conventional torque cam device, when the driving state is switched, the long groove and the pin are contacted in the circumferential direction, so that an impact torque is generated, and there is no possibility of a shock occurring when the driving state is switched. Thereby, generation | occurrence | production of the shock at the time of switching can be suppressed.

  In the above embodiment, the tooth clutch is used for the driving side engaging means and the driven side engaging means, but the present invention is not limited to this. For example, a friction clutch may be used for the driving side engaging means and the driven side engaging means. In this case, friction plates are alternately provided between the input side drive cam member 74 and the output side driven cam member 76 and the output member 75, and the input side drive cam member 74 and the output side are provided with respect to the output member 75. The driven cam member 76 moves in one of the axial directions, and friction force generated when adjacent friction plates come into contact with each other between the first cam device 71 and the secondary movable sheave 63 that is a thrust member. Engagement or engagement between the second cam device 72 and the secondary movable sheave 63 that is a thrust member may be performed. In the case of the friction clutch, the relative rotation of the first cam device or the second cam device when the driving state is switched is such that the input side driving cam member 74 and the output side driven cam member 76 are axially moved with respect to the output member 75. By moving in one direction, the input side drive cam member 74 and the output side driven cam member 76 rotate relative to the output member 75 until the adjacent friction plates come into contact with each other. Therefore, the conventional torque cam device having the cam surface facing in the circumferential direction is smaller than the relative rotation when switching from driven to driven. Therefore, the relative rotation of the first cam device or the second cam device that occurs when the torque cam device 70 is switched to the drive state can be further suppressed.

  Further, in the above embodiment, the driving side elastic member 73d and the driven side elastic member 73e are used as the driving side pressing force generating means and the driven side pressing force generating means, but the present invention is not limited to this. For example, instead of housing the drive side elastic member 73d and the driven side elastic member 73e between the storage space portion 74b and the storage space portion 77a and between the storage space portion 76b and the storage space portion 79a, respectively, Used as oil chamber and driven-side oil chamber. Then, hydraulic oil is supplied as a working fluid from a hydraulic oil supply control device (not shown) to the driving-side oil chamber and the driven-side oil chamber, and the pressing forces P1, P2 are respectively applied to the input-side driving cam member 74 by the hydraulic pressure of the hydraulic oil. Further, it may act on the output side driven cam member 76.

  In the above embodiment, the secondary oil chamber 64 and the torque cam device 70 are used as the belt clamping pressure generating means on the secondary side, but the present invention is not limited to this, and the torque cam device 70 is used as the belt clamping pressure generating means on the secondary side. You may use only. Further, as the secondary side belt clamping pressure generating means, for example, an electric motor such as a motor may be used in combination with the torque cam device 70.

  Moreover, in the said Example, although the torque cam apparatus 70 is arrange | positioned in the circumferential direction on the outer side of the secondary oil chamber 64, it is not limited to this. For example, a plurality may be arranged in the circumferential direction inside the secondary oil chamber 64. That is, the torque cam device 70 may be disposed in the secondary oil chamber 64. In this case, the hydraulic oil in the secondary oil chamber 64 can always be supplied to the torque cam device 70. Therefore, it is not necessary to newly form an oil passage for supplying hydraulic oil necessary for lubricating the torque cam device 70.

It is a skeleton figure of a belt type continuously variable transmission provided with a torque cam device concerning this invention. It is a figure which shows the torque cam apparatus at the time of no load and a drive. It is a figure which shows the 1st cam apparatus at the time of no load and a drive. It is a figure which shows the 2nd cam apparatus at the time of no load and a drive. It is a figure which shows the structural example of a switching member. It is a figure which shows the torque cam apparatus at the time of driven. It is a figure which shows the 1st cam apparatus at the time of driven. It is a figure which shows the 2nd cam apparatus at the time of driven.

Explanation of symbols

1 Belt type continuously variable transmission 10 Internal combustion engine (drive source)
20 Transaxle 30 Torque converter 40 Forward / reverse switching mechanism 50 Primary pulley 51 Primary pulley shaft 52 Primary fixed sheave 53 Primary movable sheave 54 Primary oil chamber 55 Primary partition wall 60 Secondary pulley 61 Secondary pulley shaft 62 Secondary fixed sheave 63 Secondary movable sheave 64 Secondary Oil chamber 65 Secondary partition wall 70 Torque cam device 71 First cam device 72 Second cam device 73 Switching device 73a Switching member 73b Drive-side tooth clutch (drive-side engagement means)
73c Driven side clutch (driven side engagement means)
73d Drive-side elastic member (drive-side pressing force generating means)
73e Driven side elastic member (driven side pressing force generating means)
73f Switching member rotating shaft 73g Switching elastic member 74 Input side driving cam member 74a Driving cam surface 75 Output member (output side driving cam member, input side driven cam member)
75a Output-side drive cam portion 75b Drive-side cam roller 75c Input-side driven cam portion 75d Drive-side cam roller 76 Output-side driven cam member 76a Drive-side cam surface 77 Drive-side cam holding member 78 Intermediate member 79 Drive-side cam holding member 80 Final reduction gear 90 Power transmission path 91 Power transmission shaft 100 Belt 110 Wheel

Claims (4)

It has an input-side drive cam member and an output-side drive cam member, and transmits the driving force during driving and thrust in one of the axial directions by contact between the input-side drive cam member and the output-side drive cam member. A first cam device for generating
An input-side driven cam member and an output-side driven cam member that are formed integrally with the output-side driving cam member, and contacted by the input-side driven cam member and the output-side driven cam member; A second cam device for transmitting a driven force during driving and generating a thrust in one of the axial directions;
Switching means for switching between engagement between the first cam device and the thrust member to which the generated thrust is transmitted, and engagement between the second cam device and the thrust member;
A torque cam device comprising: The switching means is
Drive-side engagement means for engaging the input-side drive cam member with the thrust member by moving the input-side drive cam member in one of the axial directions with respect to the thrust member;
The driven-side engagement that engages the output-side driven cam member and the thrust member by moving the output-side driven cam member in one of the axial directions with respect to the thrust member. Means,
In the direction in which the input side drive cam member and the output side drive cam member are in contact with each other, and in the direction in which the input side drive cam member is moved in one of the axial directions with respect to the output side drive cam member, Driving-side pressing force generating means for pressing the input-side driving cam member;
A direction in which the input-side driven cam member and the output-side driven cam member are brought into contact with each other, and the output-side driven cam member is moved in one of the axial directions with respect to the input-side driven cam member. Driven side pressing force generating means for pressing the output side driven cam member in a direction to be
Switching that restricts movement in one of the other axial directions when allowing movement in one of the axial directions of either the input side driving cam member or the output side driven cam member Members,
The torque cam device according to claim 1, comprising:   3. The torque cam device according to claim 1, wherein the switching unit engages the first cam device with the thrust target member when there is no load. 4. at least,
Two pulley shafts arranged in parallel and transmitting output torque from a driving source to one of them, two movable sheaves sliding in the axial direction on the two pulley shafts, and the two movable sheaves Two pulleys each comprising two fixed sheaves facing each other in the axial direction,
A belt for transmitting the driving force from the driving source transmitted to one of the two pulleys to the other pulley;
The torque cam device according to any one of claims 1 to 3, wherein a belt clamping pressure is generated between the movable sheave and the fixed sheave.
A belt type continuously variable transmission.

Images